US4421496A - Drive coupling - Google Patents

Drive coupling Download PDF

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Publication number
US4421496A
US4421496A US06/399,191 US39919182A US4421496A US 4421496 A US4421496 A US 4421496A US 39919182 A US39919182 A US 39919182A US 4421496 A US4421496 A US 4421496A
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US
United States
Prior art keywords
pair
jaws
connecting bolts
solid member
flexible disc
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US06/399,191
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English (en)
Inventor
Reginald S. Emerson
Norman Morris
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Individual
Original Assignee
Individual
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Filing date
Publication date
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Application granted granted Critical
Publication of US4421496A publication Critical patent/US4421496A/en
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • F02M39/02—Arrangements of fuel-injection apparatus to facilitate the driving of pumps; Arrangements of fuel-injection pumps; Pump drives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M65/00—Testing fuel-injection apparatus, e.g. testing injection timing ; Cleaning of fuel-injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/72—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members with axially-spaced attachments to the coupling parts

Definitions

  • This invention relates to drive couplings, and is especially (but not exclusively) concerned with readily-disconnectable drive couplings for connecting a drive shaft in or on a fuel injection pump test machine to the driven shaft of a fuel injection pump under test on the machine.
  • FIG. 1 shows the coupling in vertical section
  • FIG. 2 is a section taken on the line II--II in FIG. 1.
  • FIG. 1 It thus comprises a plate 10 having a shaft 12 for connection to the shaft of an electric drive motor or other prime mover in a fuel injection pump test machine.
  • the plate 10 is connected by two bolts or screws 14 to a relatively thin flexible disc 16 arranged transversely of the rotational axis 18 of the shaft 12, the bolts 14 being angularly spaced by 180°.
  • Two further bolts 20 angularly spaced at 90° to the two bolts 14 connect the disc 16 to an intermediate solid member 22.
  • Two clamping jaws 32 swivel on two pins 34 protruding from the solid member 30, the two pins 34 being formed as integral extensions of the bolts 28.
  • the jaws 32 lie one on either side of the drive axis 18 and are brought towards each other by means of a transverse bolt 36 passing through each jaw.
  • the jaws are adapted to clamp onto two drive dogs 38 forming part of an injection pump driven member 40 having a shaft 42.
  • the discs 16, 26 are relatively free to bend in planes at right angles to each pair of bolts 14, 20; 24, 28, the discs have conical flexibility whilst remaining relatively stiff torsionally.
  • the end effect is that the coupling can accommodate either angular out-of-line shafts or laterally misaligned shafts whilst ensuring high torsional stiffness.
  • the jaws 32 offer the facility of rapid connection of the coupling to the article to be driven (in this case the shaft of a fuel pump on a fuel injection pump test machine).
  • the above-described coupling has, however, certain disadvantages.
  • the spring discs in order to give sufficient lateral flexibility, the spring discs must be spaced a sufficient distance apart so as not to become over-stressed in bending when allowing for a specific amount of mal-alignment of the shafts. This makes the coupling inconveniently long.
  • the jaws 32 having flat interacting surfaces 44, only lend themselves to clamping rectangular-shaped dogs 38 on the driven member 40.
  • the coupling is of restricted application.
  • backlash is frequently encountered in the coupling because of the torsional free movement occasioned by the clearance which must exist between the pins 34 on which the jaws 32 swivel and the pin-receiving holes in the jaws.
  • the invention is directed to a drive coupling incorporating at least one flexible disc and a pair of jaws for clamping dogs on a driven member, the jaws being mounted for limited pivotal movement on respective pins which are received in corresponding holes in the jaws, in which slots break into the said holes from the peripheral surfaces of the jaws so that, when the jaws are tightened onto the dogs of a driven member, any clearance between the pins and the holes is taken up, and backlash between them is obviated.
  • the invention is directed to a drive coupling having two spaced-apart flexible discs and two solid members connected to those discs, in which the two solid members are located between the discs and overlap each other axially of the coupling so as to shorten the coupling.
  • the invention also extends, in a third aspect, to a drive coupling comprising a pair of jaws for clamping dogs on a driven member, in which the dog-engaging surfaces of the jaws are of curved convex shape so as to be capable of gripping dogs having concave surfaces as well as dogs of rectangular shape.
  • FIGS. 3 to 8 of the accompanying drawings An example of a drive coupling in accordance with the invention is shown in FIGS. 3 to 8 of the accompanying drawings.
  • FIG. 1 is a cross-section of a prior art coupling.
  • FIG. 2 is a section along line II--II of FIG. 1.
  • FIG. 3 is a vertical section similar to FIG. 1;
  • FIG. 4 is a section taken on the line IV--IV in FIG. 3;
  • FIG. 5 is a plan view along the arrow V in FIG. 4;
  • FIG. 6 is a perspective view of one of the jaws shown in FIG. 4;
  • FIG. 7 is an enlarged version of FIG. 4 showing the jaws gripping two rectangular-shaped dogs of a driven member
  • FIG. 8 is a view similar to FIG. 7 showing the jaws gripping two of six concave-surfaced dogs on a driven member.
  • the drive coupling shown in FIGS. 3 to 6 is designed, like that shown in FIGS. 1 and 2, to couple the drive shaft of an electric motor or other prime mover on or in a fuel injection pump test machine to the driven shaft of a fuel injection pump under test. It is to be understood, however, that the coupling of FIGS. 3 to 6 is not restricted to such use, but can be applied to any installation or equipment where a readily-releasable coupling providing lateral flexibility with torsional stiffness is called for.
  • FIGS. 3 to 6 Certain parts shown in FIGS. 3 to 6 are substantially identical to corresponding parts shown in FIGS. 1 and 2, and the same reference numerals have therefore been used for them. It will be seen, however, that the two spaced-apart flexible discs 16 and 26 in FIG. 3 are bolted to solid members 46 and 48 which are differently shaped from the solid members 22 and 30 shown in FIG. 1 and which are both located between the discs and overlap one another in an axial direction. To permit such overlap, the solid member 46 has a deep transversely-extending groove 50 formed in it (see FIG. 5), while the solid member 48 is shaped as a rectangular elongate bar which is received with ample clearance wholly within the groove 50.
  • the solid member 46 has screw-headed bore holes (not shown) in it.
  • the bolts or screws 52 have extensions 56 serving as pins on which a pair of clamping jaws 58 are mounted for limited pivotal movement.
  • the jaws 58 are movable towards and away from each other by rotation of a transverse bolt 36, as in the coupling of FIGS. 1 and 2.
  • a coiled compression spring 60 surrounds the mid-portion of the bolt 36 (see FIGS. 7 and 8).
  • FIGS. 3 to 8 has three important advantages over that shown in FIGS. 1 and 2.
  • the length of the coupling is substantially reduced by locating the second solid member 48 upstream of the second flexible disc so that both it and the first solid member 46 lie between the two discs 16 and 26.
  • This feature diminishes the overall length of the coupling because the space required for the second solid member 48 (which space, in the coupling of FIGS. 1 and 2, contributes to coupling length) is now sited between the flexible discs and does not contribute to coupling overall length, especially as the second solid member 48 is received wholly within the groove 50 in the first solid member 46.
  • a second advantage of the coupling shown in FIGS. 3 to 8 is that torsional free movement or backlash between the pins 56 and the jaws 58 is obviated by providing slots 62 substantially parallel with the abutment faces 64 of the jaws and breaking into the drive pin holes 66 in the jaws from the peripheral surfaces 68. This permits the tension in the jaw clamping bolt 36 to deflect the jaws in the regions 70 of the jaws so as to take up the clearance between the pins 56 and the holes 66 in the jaws.
  • the third advantage given by the coupling of FIGS. 3 to 8 is that, as shown in FIG. 8, the shape of the jaws is such that they can clamp the concave cylindrically-shaped surfaces 72 of the dogs 74 provided on a six-dog Simms coupling 76 whilst at the same time remaining suitable for clamping rectangular-shaped dogs 78 of a pump driven member 80 as shown in FIG. 7.
  • the six dogs 74 shown in FIG. 8 two opposing dogs are clamped between the jaws 58, while the remaining four are received, with clearance, in recesses 82 in the jaws.
  • spacing sleeves 84 which surround the bolts or screws 14, 20, 52 and 54. If desired, however, these spacing sleeves could be replaced by projections on the plate 10 and the member 48 in FIG. 3, and on the members 46 and 48 in FIG. 5.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Mechanical Operated Clutches (AREA)
  • Flexible Shafts (AREA)
  • Surgical Instruments (AREA)
US06/399,191 1979-06-29 1982-07-16 Drive coupling Expired - Fee Related US4421496A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB7922650 1979-06-29
GB7922650A GB2052013B (en) 1979-06-29 1979-06-29 Drive coupling

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
US06162663 Continuation 1980-06-24

Publications (1)

Publication Number Publication Date
US4421496A true US4421496A (en) 1983-12-20

Family

ID=10506175

Family Applications (1)

Application Number Title Priority Date Filing Date
US06/399,191 Expired - Fee Related US4421496A (en) 1979-06-29 1982-07-16 Drive coupling

Country Status (8)

Country Link
US (1) US4421496A (de)
JP (1) JPS566923A (de)
AT (1) AT371225B (de)
DE (1) DE3024004A1 (de)
ES (1) ES8103295A1 (de)
FR (1) FR2460418B1 (de)
GB (1) GB2052013B (de)
IT (1) IT1143024B (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4601601A (en) * 1983-07-20 1986-07-22 Leslie Hartridge Limited Rotary anti-backlash component
US5240180A (en) * 1991-06-07 1993-08-31 Societe Anonyme Aerospatiale Societe Nationale Industrielle Water film cooling modular nozzle particularly for high temperature testing of specimens or similar
US5490020A (en) * 1993-06-10 1996-02-06 International Business Machines Corporation High torsional stiffness low axial deflection stiffness drive shaft system
WO2003042529A1 (de) * 2001-11-12 2003-05-22 Robert Bosch Gmbh Verteilereinspritzpumpe mit vorgespanntem kraftübertragungselement
US6648764B2 (en) * 1999-05-06 2003-11-18 Kabushiki Kaisha Yaskawa Denki Leaf spring type coupling and motor device using the coupling
RU181846U1 (ru) * 2017-11-03 2018-07-26 Публичное акционерное общество "КАМАЗ" Привод топливного насоса высокого давления двигателя внутреннего сгорания

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61108524U (de) * 1984-12-21 1986-07-09
DE3719900C2 (de) * 1987-06-13 1996-09-19 Bosch Gmbh Robert Antriebskupplung

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1246445A (en) * 1917-02-06 1917-11-13 Edwin H Ludeman Flexible shaft-coupling.
US2745267A (en) * 1952-02-11 1956-05-15 Hagenlocher Ernest Torsionally resilient flexible couplings
US2790312A (en) * 1952-03-31 1957-04-30 Hagenlocher Ernest Flexible couplings
US2932255A (en) * 1955-07-26 1960-04-12 Lora H Neukirch Eccentric drive mechanism
US3229480A (en) * 1964-09-10 1966-01-18 Midland Ross Corp Flexible coupling
US3230738A (en) * 1962-10-11 1966-01-25 Midland Ross Corp Flexible coupling for shafts
US4196597A (en) * 1976-05-21 1980-04-08 Burmah Engineering Company Limited Flexible shaft couplings with axially spaced diaphragms
US4202183A (en) * 1976-09-29 1980-05-13 Robert Bosch Gmbh Gear coupling

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB330814A (en) * 1929-07-30 1930-06-19 Birmingham Small Arms Co Ltd Improvements in or relating to universal joints or couplings
US2371507A (en) * 1942-01-21 1945-03-13 Romec Pump Company Coupling
GB1283723A (en) * 1969-10-14 1972-08-02 Kaman Aerospace Corp Flexible coupling
JPS493872U (de) * 1972-04-10 1974-01-14
CH592825A5 (de) * 1976-08-25 1977-11-15 Bbc Brown Boveri & Cie

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1246445A (en) * 1917-02-06 1917-11-13 Edwin H Ludeman Flexible shaft-coupling.
US2745267A (en) * 1952-02-11 1956-05-15 Hagenlocher Ernest Torsionally resilient flexible couplings
US2790312A (en) * 1952-03-31 1957-04-30 Hagenlocher Ernest Flexible couplings
US2932255A (en) * 1955-07-26 1960-04-12 Lora H Neukirch Eccentric drive mechanism
US3230738A (en) * 1962-10-11 1966-01-25 Midland Ross Corp Flexible coupling for shafts
US3229480A (en) * 1964-09-10 1966-01-18 Midland Ross Corp Flexible coupling
US4196597A (en) * 1976-05-21 1980-04-08 Burmah Engineering Company Limited Flexible shaft couplings with axially spaced diaphragms
US4202183A (en) * 1976-09-29 1980-05-13 Robert Bosch Gmbh Gear coupling

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4601601A (en) * 1983-07-20 1986-07-22 Leslie Hartridge Limited Rotary anti-backlash component
US5240180A (en) * 1991-06-07 1993-08-31 Societe Anonyme Aerospatiale Societe Nationale Industrielle Water film cooling modular nozzle particularly for high temperature testing of specimens or similar
US5490020A (en) * 1993-06-10 1996-02-06 International Business Machines Corporation High torsional stiffness low axial deflection stiffness drive shaft system
US5625510A (en) * 1993-06-10 1997-04-29 International Business Machines Corporation High torsional stiffness low axial deflection stiffness drive shaft
US6648764B2 (en) * 1999-05-06 2003-11-18 Kabushiki Kaisha Yaskawa Denki Leaf spring type coupling and motor device using the coupling
WO2003042529A1 (de) * 2001-11-12 2003-05-22 Robert Bosch Gmbh Verteilereinspritzpumpe mit vorgespanntem kraftübertragungselement
RU181846U1 (ru) * 2017-11-03 2018-07-26 Публичное акционерное общество "КАМАЗ" Привод топливного насоса высокого давления двигателя внутреннего сгорания

Also Published As

Publication number Publication date
ATA333080A (de) 1982-10-15
JPS6331007B2 (de) 1988-06-22
IT8049099A0 (it) 1980-06-27
GB2052013A (en) 1981-01-21
GB2052013B (en) 1983-03-09
JPS566923A (en) 1981-01-24
DE3024004A1 (de) 1981-01-15
FR2460418A1 (fr) 1981-01-23
IT1143024B (it) 1986-10-22
ES492737A0 (es) 1981-02-16
AT371225B (de) 1983-06-10
FR2460418B1 (fr) 1988-05-06
ES8103295A1 (es) 1981-02-16

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